US4335586A - Shaft-disc assembly - Google Patents

Shaft-disc assembly Download PDF

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Publication number
US4335586A
US4335586A US06/092,039 US9203979A US4335586A US 4335586 A US4335586 A US 4335586A US 9203979 A US9203979 A US 9203979A US 4335586 A US4335586 A US 4335586A
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United States
Prior art keywords
shaft
disc
assembly
centering
webs
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US06/092,039
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English (en)
Inventor
Richard Kochendorfer
Helmut Vogler
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Deutsches Zentrum fuer Luft und Raumfahrt eV
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Deutsches Zentrum fuer Luft und Raumfahrt eV
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Publication of US4335586A publication Critical patent/US4335586A/en
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Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/025—Fixing blade carrying members on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end

Definitions

  • the present invention relates to a shaft-disc assembly where the disc is mounted coaxially on the shaft for rotation therewith.
  • An example of such an assembly is a disc-shaped turbine wheel on a turbine shaft.
  • the turbine wheel was constructed substantially thicker in the region close to the axis than in the region remote from the axis, so that by the thickening of the turbine wheel hub a higher tensile loading could be achieved.
  • Such constructions are known for example from Patent Application P No. 24 60 739.4 and from the following literature sources:
  • An object of the present invention is to construct a shaft-disc assembly, such as a disc-shaped turbine wheel on a turbine shaft, in such a manner, that a rotation-secured and centered mounting of the turbine wheel on the shaft is achieved without additional dimensional increases of the turbine wheel, the linkage between the disc and the shaft ensuring rupture-free operation of the unit even at high temperatures and at high speeds of rotation.
  • a shaft and disc assembly the disc being mounted coaxially on the shaft for rotation therewith, the assembly comprising a shaft, a disc with a central aperture having an internal diameter greater than the external diameter of the shaft and radial slots extending from the central aperture, a centering element mounted on the shaft, webs on the centering element extending substantially parallel to the shaft axis and lying against the internal surface of the central disc aperture, which webs, under the action of centrifugal force when the assembly is rotating can be resiliently pressed against said internal surface, and tongues rigidly fixed to the shaft and extending radially therefrom to project into the radial slots of the disc.
  • a faultless centering of the turbine wheel on the shaft can be achieved, independently of the different thermal expansions of disc and shaft, respectively, and independently of mechanical deformation resulting from the centrifugal forces arising at high speeds of rotation.
  • the radially projecting tongues makes possible a form-locking rotary connection, the disc being displaceable in a radial direction relative to these tongues. For this reason, this connection is also free of disturbances due to differing mechanical deformations at high temperatures and high speeds of rotation.
  • FIG. 1 is a perspective, schematic exploded view of a shaft-disc assembly
  • FIG. 2 is an axial partly sectional view of the shaft-disc assembly of FIG. 1;
  • FIG. 3 is a sectional view of an alternative embodiment of a shaft-disc assembly in a plane extending parallel to the disc;
  • FIG. 4 is a partial longitudinal section of a further alternative embodiment of a shaft-disc assembly.
  • a plurality of radially outward-projecting tongues 2 are secured against rotation to a steel shaft 1, either in the manner shown in FIG. 3 by direct attachment to the shaft or in the manner apparent in FIGS. 1 and 4 by fitting of a sleeve 3 on the shaft 1 and rotation-secure connection of the two parts, in which case the sleeve 3 carries the radially outward projecting tongues 2.
  • the radially outward-projecting tongues 2 engage with their free ends, in the manner shown in FIG. 3, into slots 4 between circular segments 5, which in their totality make up a turbine wheel 6.
  • the inner faces of the circular segments lie against webs 7, 7a extending parallel to shaft 1, which webs are fastened to a circular front-end face 8, 8a, respectively.
  • the faces 8 and 8a have central passage bores 9, 9a, respectively, with an internal diameter which is slightly greater than the external diameter of the shaft 1.
  • the sub-units composed of front-end faces 8 and 8a and webs 7, 7a will be referred to as centering sockets 10 and 10a, respectively. They are slipped from both sides of the fastening region on the shaft 1 in such a manner, that in each case the webs 7 and 7a of one centering socket 10 or 10a engage into gaps 11a or 11, respectively, of the other centering socket 10a or 10.
  • the centering sockets 10 and 10a are pressed from both sides against the front-end face of sleeve 3 by means of pressure flanges 12 and 12a, respectively, slipped on the shaft.
  • the pressure flange 12a bears with its shaft 13 against a stop 13a fast with the shaft 1, whilst a nut 14, which is screwed on an external thread 15 or shaft 1, presses the pressure flange 12 against the pressure flange 12a. In this manner, a securing of the centering sockets against axial displacements is obtained.
  • FIG. 4 shows an embodiment where the pressure flanges and the webs 7, 7a are formed in one and the same member 110, 110a.
  • the sectors are surrounded by a ceramic ring 16.
  • the construction of the turbine wheel is only partly shown in FIG. 3; as can be seen, the ceramic ring 16 has connected thereto schematically illustrated turbine blades 17, which may be encircled by a not shown shrunk-on hoop.
  • the pressure flanges 12 and 12a have, on their side facing towards the turbine wheel and outside the centering sockets, annular grooves 18 and 18a, respectively, into which an elastically compressible material 19 and 19a is located, which, on one hand, bears against the bottom of the annular groove and, on the other hand, against the turbine wheel.
  • This material may for example be a wire plait. It makes possible a displacement of the turbine wheel relative to the pressure flanges 12 and 12a in radial direction.
  • the circular segments of the turbine wheel consist preferably of a ceramic material.
  • the two centering sockets consist of an elastic, preferably metallic material.
  • the webs 7 and 7a are only connected at one end with the corresponding front-end face of the centering sockets, the other end is free. Owing to this, during rotation of the shaft and with it of the centering sockets, the webs bend resiliently outwards, so that they apply with a frictional locking effect against the inner face of the turbine wheel 6 formed of circular segments 5, thus safely centering the wheel even at higher speeds of rotation. At the same time, all relative displacements of the turbine wheel and of the shaft as well as of the centering sockets, which arise due to differing thermal expansion coefficients and different ductility under the influence of centrifugal forces, are compensated.
  • FIG. 4 is essentially similar in construction to the embodiment described with reference to FIGS. 1 to 3, for which reason corresponding parts bear the same reference numerals.
  • the sole difference consists in that the centering sockets assume simultaneously also the function of the pressure flanges, that is to say, the pressure flanges and the centering sockets are integrally constructed. This allows a further simplification of assembly.
  • the two centering sockets as a centering element in one piece in the form of a cage, which has webs interconnecting the two end faces.
  • the only essential feature of the centering element is that the webs must be given the possibility of moving radially outwards under the influence of the centrifugal force, so that they are urged at any speed with an elastic force against the inner face of the circular segments.
  • this will be achieved more advantageously with a construction comprising webs free at one end than with a cage-like construction.
  • the centering sockets In order to ensure the elastic deformability of the webs, it is advantageous to make the centering sockets from a ductile material.
  • the turbine wheel illustrated in the drawings consists of a plurality of circular segments. It is also possible to employ a one-piece turbine wheel having corresponding radial slots, which however do not fully divide the individual regions of the turbine wheel into circular segments.
  • the elastic material between the pressure flanges which preferably consists of a thermally highly resistant elastic steel wire plait, also prevents effectively oscillations of the turbine wheel segments.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
US06/092,039 1978-11-08 1979-11-07 Shaft-disc assembly Expired - Lifetime US4335586A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2848355A DE2848355C2 (de) 1978-11-08 1978-11-08 Wellen-Naben-Verbindung
DE2848355 1978-11-08

Publications (1)

Publication Number Publication Date
US4335586A true US4335586A (en) 1982-06-22

Family

ID=6054104

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/092,039 Expired - Lifetime US4335586A (en) 1978-11-08 1979-11-07 Shaft-disc assembly

Country Status (4)

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US (1) US4335586A (de)
JP (1) JPS6029015B2 (de)
DE (1) DE2848355C2 (de)
GB (1) GB2034440B (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5324234A (en) * 1992-07-09 1994-06-28 Kay Seven Co., Ltd. Shaft coupling
US5862706A (en) * 1996-07-16 1999-01-26 Mcdonnell Douglas Helicopter Company Shaft deflection controller
US20020028142A1 (en) * 1999-12-03 2002-03-07 Dewhirst Randy E. Centrifugal impeller assembly
US6660407B1 (en) * 1999-07-24 2003-12-09 Daimlerchrysler Ag Friction-welded shaft-disc assembly and method for the manufacture thereof
US20040178108A1 (en) * 2001-01-19 2004-09-16 Stepac L.A., Ltd. System for packaging, storing and transporting agricultural produce
US20080153606A1 (en) * 2006-12-21 2008-06-26 Hunter Douglas Industries Bv Adjustable drive coupling for adjacent architectural coverings
US20140080610A1 (en) * 2009-12-25 2014-03-20 Oiles Corporation Shaft coupling mechanism
CN109372582A (zh) * 2018-12-16 2019-02-22 阜宁隆德机械制造有限责任公司 一种外置传动叶轮
CN115125382A (zh) * 2022-07-29 2022-09-30 国营川西机器厂 热处理装置与粉末高温合金双性能涡轮盘热处理方法
US11530723B2 (en) * 2018-09-03 2022-12-20 Hl Mando Corporation Power transmission device of steering system

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3706365C1 (de) * 1987-02-27 1988-09-15 Geesthacht Gkss Forschung Kupplung zum spielfreien und zentrierten Verbinden eines Nabenteils mit einer Welle
JPH01125160U (de) * 1988-02-16 1989-08-25
US5020932A (en) * 1988-12-06 1991-06-04 Allied-Signal Inc. High temperature ceramic/metal joint structure
US4934138A (en) * 1988-12-06 1990-06-19 Allied-Signal Inc. High temperature turbine engine structure
US6250883B1 (en) 1999-04-13 2001-06-26 Alliedsignal Inc. Integral ceramic blisk assembly
US20070185427A1 (en) * 2006-01-13 2007-08-09 Chung-Yu Lin Adhesive bandage with reduced pain during removal

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2773365A (en) * 1953-11-23 1956-12-11 George A Delf Vibration-damping hub and shaft assemblies
US2943464A (en) * 1958-04-09 1960-07-05 Fred W Voges Aligning flexible coupling
US3036412A (en) * 1959-07-16 1962-05-29 Tocci-Guilbert Berne Resilient coupling
US3084852A (en) * 1961-03-29 1963-04-09 Gen Electric Fan blade hub connector
US3096106A (en) * 1960-09-15 1963-07-02 Corduroy Rubber Company Torque transmitting bearing
US3362191A (en) * 1965-03-16 1968-01-09 M I Soc D Applic De Moulages I Elastic coupling
US4244240A (en) * 1976-12-17 1981-01-13 The Johns Hopkins University Elastic internal flywheel gimbal

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE598445C (de) * 1929-08-28 1934-06-11 Siemens Schuckertwerke Akt Ges Einrichtung zur Befestigung von Turbinenraedern auf der Welle mit Feder und Nut
DE607274C (de) * 1931-10-17 1934-12-20 Spontan Ab Dampf- oder Gasturbine
US3577795A (en) * 1969-10-27 1971-05-04 Chandler Evans Inc Means to overcome differential thermal expansion effects in bimetallic splined shaft assemblies
JPS485314U (de) * 1971-06-04 1973-01-22
JPS53101973U (de) * 1977-01-21 1978-08-17

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2773365A (en) * 1953-11-23 1956-12-11 George A Delf Vibration-damping hub and shaft assemblies
US2943464A (en) * 1958-04-09 1960-07-05 Fred W Voges Aligning flexible coupling
US3036412A (en) * 1959-07-16 1962-05-29 Tocci-Guilbert Berne Resilient coupling
US3096106A (en) * 1960-09-15 1963-07-02 Corduroy Rubber Company Torque transmitting bearing
US3084852A (en) * 1961-03-29 1963-04-09 Gen Electric Fan blade hub connector
US3362191A (en) * 1965-03-16 1968-01-09 M I Soc D Applic De Moulages I Elastic coupling
US4244240A (en) * 1976-12-17 1981-01-13 The Johns Hopkins University Elastic internal flywheel gimbal

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"Ceramics for High-Performance Applications", Proceedings of the Second A Materials Technology Conference, Hyannis, Massachusetts, Nov. 13-16, 1973.
"Ceramics for High-Performance Applications", Proceedings of the Second A Materials Technology Conference, Hyannis, Massachusetts, Nov. 13-16, 1973. *

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5324234A (en) * 1992-07-09 1994-06-28 Kay Seven Co., Ltd. Shaft coupling
US5862706A (en) * 1996-07-16 1999-01-26 Mcdonnell Douglas Helicopter Company Shaft deflection controller
US6660407B1 (en) * 1999-07-24 2003-12-09 Daimlerchrysler Ag Friction-welded shaft-disc assembly and method for the manufacture thereof
US20020028142A1 (en) * 1999-12-03 2002-03-07 Dewhirst Randy E. Centrifugal impeller assembly
US20040178108A1 (en) * 2001-01-19 2004-09-16 Stepac L.A., Ltd. System for packaging, storing and transporting agricultural produce
US8267234B2 (en) * 2006-12-21 2012-09-18 Hunter Douglas Industries Bv Adjustable drive coupling for adjacent architectural coverings
US20080153606A1 (en) * 2006-12-21 2008-06-26 Hunter Douglas Industries Bv Adjustable drive coupling for adjacent architectural coverings
US20140080610A1 (en) * 2009-12-25 2014-03-20 Oiles Corporation Shaft coupling mechanism
US9051973B2 (en) * 2009-12-25 2015-06-09 Oiles Corporation Shaft coupling mechanism
US11530723B2 (en) * 2018-09-03 2022-12-20 Hl Mando Corporation Power transmission device of steering system
CN109372582A (zh) * 2018-12-16 2019-02-22 阜宁隆德机械制造有限责任公司 一种外置传动叶轮
CN115125382A (zh) * 2022-07-29 2022-09-30 国营川西机器厂 热处理装置与粉末高温合金双性能涡轮盘热处理方法
CN115125382B (zh) * 2022-07-29 2024-01-23 国营川西机器厂 热处理装置与粉末高温合金双性能涡轮盘热处理方法

Also Published As

Publication number Publication date
GB2034440A (en) 1980-06-04
JPS55107121A (en) 1980-08-16
JPS6029015B2 (ja) 1985-07-08
GB2034440B (en) 1983-01-06
DE2848355C2 (de) 1983-08-25
DE2848355A1 (de) 1980-05-14

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